EP1637368A2 - Aufhängungseinrichtung - Google Patents

Aufhängungseinrichtung Download PDF

Info

Publication number
EP1637368A2
EP1637368A2 EP05255290A EP05255290A EP1637368A2 EP 1637368 A2 EP1637368 A2 EP 1637368A2 EP 05255290 A EP05255290 A EP 05255290A EP 05255290 A EP05255290 A EP 05255290A EP 1637368 A2 EP1637368 A2 EP 1637368A2
Authority
EP
European Patent Office
Prior art keywords
hydraulic
liquid
accumulator
flow
suspension device
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP05255290A
Other languages
English (en)
French (fr)
Other versions
EP1637368A3 (de
EP1637368B1 (de
Inventor
Motohiko c/o Toyoto Jidosha K.K. Honma
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Toyota Motor Corp
Original Assignee
Toyota Motor Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Toyota Motor Corp filed Critical Toyota Motor Corp
Publication of EP1637368A2 publication Critical patent/EP1637368A2/de
Publication of EP1637368A3 publication Critical patent/EP1637368A3/de
Application granted granted Critical
Publication of EP1637368B1 publication Critical patent/EP1637368B1/de
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
    • B60G17/02—Spring characteristics, e.g. mechanical springs and mechanical adjusting means
    • B60G17/04—Spring characteristics, e.g. mechanical springs and mechanical adjusting means fluid spring characteristics
    • B60G17/0416—Spring characteristics, e.g. mechanical springs and mechanical adjusting means fluid spring characteristics regulated by varying the resiliency of hydropneumatic suspensions
    • B60G17/0432—Spring characteristics, e.g. mechanical springs and mechanical adjusting means fluid spring characteristics regulated by varying the resiliency of hydropneumatic suspensions by varying the number of accumulators connected to the hydraulic cylinder
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2400/00—Indexing codes relating to detected, measured or calculated conditions or factors
    • B60G2400/10—Acceleration; Deceleration
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2400/00—Indexing codes relating to detected, measured or calculated conditions or factors
    • B60G2400/50—Pressure
    • B60G2400/51—Pressure in suspension unit
    • B60G2400/512—Pressure in suspension unit in spring
    • B60G2400/5122—Fluid spring
    • B60G2400/51222—Pneumatic
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2500/00—Indexing codes relating to the regulated action or device
    • B60G2500/20—Spring action or springs
    • B60G2500/206—Variable pressure accumulators for hydropneumatic suspensions
    • B60G2500/2064—Variable pressure accumulators for hydropneumatic suspensions by varying the number of accumulators connected in parallel to the hydraulic cylinder

Definitions

  • the present invention relates to a suspension apparatus.
  • Patent Document 1 Japanese Patent Application Publication No. 63-130419
  • Patent Document 2 Japanese Patent Application Publication No. 63-78806
  • Patent Document 3 Japanese Patent Application Publication No. 63-49512 discloses a suspension apparatus including a hydraulic suspension cylinder provided for a wheel of a vehicle, two accumulators connected to the suspension cylinder, and a switchable valve provided between the two accumulators.
  • the switchable valve When, in the above-indicated suspension apparatus, the switchable valve is switched between a closed state thereof and an open state thereof, the number of the accumulator(s) that communicates or communicate with the suspension cylinder is changed, and accordingly a spring constant of the two accumulators as a whole is changed between a high value and a low value.
  • An embodiment of the present invention seeks to provide a suspension apparatus which includes a hydraulic suspension device and at least two accumulators and which prevents a system hydraulic pressure from being excessively increased.
  • the claimable modes include at least respective modes corresponding to the appended claims, but may additionally include broader or narrower modes of the present invention, or even one or more different inventions than the present invention.
  • Each of the following modes (1) through (8) is numbered like the appended claims, and depends from the other mode or modes, where appropriate, so as to help understand the claimable modes and to indicate and clarify possible combinations of elements or technical features thereof. It is, however, to be understood that the present invention is not limited to the elements or technical features of the following modes, or the combinations thereof, that will be described below for illustrative purposes only.
  • a suspension apparatus for use in a vehicle including a body, a body-side member, a wheel, and a wheel-side member, the apparatus comprising a hydraulic suspension device which is adapted to be provided between the body-side member and the wheel-side member; a first liquid passage; a first connection portion; a first accumulator which is connected to the first liquid passage via the first connection portion and is connected to the hydraulic suspension device via the first connection portion and the first liquid passage; a second liquid passage; a second connection portion; a second accumulator which is connected to the second liquid passage via the second connection portion and is connected to the first liquid passage via the second connection portion and the second liquid passage; and a liquid-flow control device which controls a flow of a hydraulic liquid between the hydraulic suspension device and at least one of the first and second accumulators, wherein in a state in which the liquid-flow control device allows the hydraulic liquid to flow from the hydraulic suspension device into each of the first and second accumulators, the first liquid passage and the first connection portion allow the hydraulic liquid to more easily flow therethrough into
  • At least two hydraulic accumulators including the first and second accumulators are connected, in parallel, to the hydraulic suspension device. More specifically described, the first accumulator is connected to the suspension device via the first liquid passage, and the second accumulator is connected to the suspension device via the second liquid passage.
  • the present invention is applicable to two hydraulic accumulators out of the three or more hydraulic accumulators.
  • the liquid-flow control device controls the flow of the hydraulic liquid between the hydraulic suspension device and the first and/or second accumulators.
  • the liquid-flow control device is selectively operable in a first mode thereof in which the control device allows the hydraulic liquid to flow between the hydraulic suspension device and each of the first and second accumulators, and a second mode thereof in which the control valve allows the hydraulic liquid to flow between the hydraulic suspension device and the second accumulator and inhibits the hydraulic liquid from flowing between the hydraulic suspension device and the first accumulator.
  • the liquid-flow control device will be described later.
  • the first liquid passage and the first connection portion allow the hydraulic liquid to more easily flow therethrough into the first accumulator than the second liquid passage and the second connection portion allow the hydraulic liquid to flow therethrough into the second accumulator.
  • the first liquid passage and the first connection portion have a lower resistance to the flow of the hydraulic liquid therethrough than that of the second liquid passage and the second connection portion.
  • the common portion should be added to the second liquid passage, or should be subtracted from the first liquid passage.
  • the shapes or dimensions of the first liquid passage and the first connection portion are so determined as to have the lower flow resistance than the flow resistance the shapes or dimensions of the second liquid passage and the second connection portion are so determined as to have. More specifically described, a transverse cross-section area of each of the first liquid passage and the first connection portion may be larger than that of each of the second liquid passage and the second connection portion, or the first liquid passage may be is shorter than the second liquid passage.
  • the hydraulic liquid can more easily flow into the first accumulator than into the second accumulator. That is, when a certain amount of the hydraulic liquid flows out of the hydraulic suspension device, a greater amount of the hydraulic liquid flows into the first accumulator and a smaller amount of the hydraulic liquid flows into the second accumulator, as compared with a case where the hydraulic liquid can flow, with a same degree of ease, into the first and second accumulators. Thus, the pressure in the second accumulator can be prevented from being excessively increased.
  • the pressure in the first accumulator is increased by a greater amount; and since the smaller amount of the hydraulic liquid flows into the second accumulator, the pressure in the second accumulator is increased by a smaller amount.
  • the second accumulator has a spring constant higher than that of the first accumulator, the pressure in the first accumulator is increased by an off-set or restrained amount and similarly the pressure in the second accumulator is increased by an off-set or restrained amount.
  • the hydraulic pressure in the present suspension apparatus i.e., in the first and second liquid passages (this hydraulic pressure will be referred to as the "system pressure" where appropriate) can be effectively prevented from being excessively increased, and accordingly the suspension apparatus can be avoided from being subjected to an excessively great force.
  • the second elastic body has the higher spring constant than that of the first elastic body.
  • a volume of the second elastic body is smaller than that of the first elastic body.
  • each of the first and second accumulators includes a housing; and a partition member which separates an inner space of the housing into two portions one of which provides a hydraulic chamber filled with the hydraulic liquid and an other of which accommodates an elastic body elastically pressing, via the partition member, the hydraulic liquid filling the hydraulic chamber.
  • the partition member may be provided by a flexible member such as bellows, a diaphragm, or a bladder; or a piston.
  • the elastic body may be provided by a spring.
  • the spring constant of the first or second accumulator can be increased or decreased by decreasing or increasing a volume of the pressurized gas charged into the accumulator while a pressure of the gas is not changed; and in the case where the elastic body is provided by a spring, the spring constant of the first or second accumulator can be increased or decreased by increasing or decreasing a spring constant of the spring.
  • a transverse cross-section area of at least a portion of at least one of the second liquid passage and the second connection portion is smaller than that of the first liquid passage and the first connection portion. That is, the second liquid passage or the second connection portion includes the portion having the smallest cross-section area in the second liquid passage, the second connection portion, the first liquid passage, and the first connection portion. In other words, one of the smaller one of the respective cross-section areas of the first liquid passage and the first connection portion is larger than the smaller one of the respective cross-section areas of the second liquid passage and the second connection portion. Consequently the hydraulic liquid can more easily flow into the first accumulator than into the second accumulator.
  • the ratio, S J1 /S J2 , of the transverse cross-section area S J1 of the first connection portion (smaller than the transverse cross-section area S P1 of the first liquid passage) to the transverse cross-section area S J2 of the second connection portion (smaller than the transverse cross-section area S P2 of the second liquid passage) be not smaller than 2 or not smaller than 3, more preferably, not smaller than 4, not smaller than 6, or not smaller than 10, on one hand, and not greater than 36, not greater than 30, or not greater than 20.
  • the liquid-flow control device includes at least one control valve which is provided between the first accumulator and a third connection portion where the second liquid passage is connected to the first liquid passage, and which is selectively switchable to (a) a communication state thereof in which said at least one control valve causes the hydraulic suspension device to communicate with the first accumulator and thereby allows the hydraulic liquid to flow from the hydraulic suspension device to the first accumulator and flow from the first accumulator to the hydraulic suspension device, and (b) a conditional inhibition state thereof in which said at least one control valve inhibits, when a pressure difference obtained by subtracting, from a pressure of the hydraulic liquid in a first portion of the first liquid passage that is located between said at least one control valve and the hydraulic suspension device, a pressure of the hydraulic liquid in a second portion of the first liquid passage that is located between said at least one control valve and the first accumulator does not exceed a pre-set pressure, the hydraulic liquid from flowing between the hydraulic suspension device and the first accumulator and
  • the hydraulic pressure in the second portion of the first liquid passage that is located on the side of the first accumulator is smaller than the pre-set pressure (e.g., a biasing pressure produced by a spring)
  • the hydraulic liquid is inhibited from flowing between the hydraulic suspension device and the first accumulator, while the hydraulic liquid is allowed to flow between the hydraulic suspension device and the second accumulator. Since the hydraulic suspension device communicates with the second accumulator only, the spring constant of the two accumulators as a whole is, in fact, equal to a spring constant of the second accumulator and accordingly is high.
  • an amount of operation of the hydraulic suspension device e.g., a stroke of a piston rod of the so-called hydraulic suspension cylinder
  • an amount of relative displacement of the body-side member and the wheel-side member in the vertical direction can be small.
  • the hydraulic liquid When the above-indicated pressure difference exceeds the pre-set pressure, the hydraulic liquid is allowed to flow from the hydraulic suspension device to the first accumulator but is inhibited from flowing from the first accumulator to the hydraulic suspension device. Thus, the hydraulic liquid is allowed to flow from the hydraulic suspension device into each of the first and second accumulators. Since the hydraulic liquid can more easily flow into the first accumulator than into the second accumulator, a greater amount of the hydraulic liquid flows into the first accumulator and a smaller amount of the liquid flows into the second accumulator, as compared with the case where the hydraulic liquid can flow, with the same degree of ease, into each of the first and second accumulators. In a particular case where the spring constant of the second accumulator is higher than that of the first accumulator, the system pressure of the present suspension apparatus can be effectively prevented from being excessively increased.
  • the liquid-flow control device comprises (a) a solenoid-operated valve which is provided in the first liquid passage and includes a solenoid and which is selectively switchable to at least an open state thereof and a closed state thereof, when an electric current supplied to the solenoid is controlled, and (b) a relief valve which is provided in parallel with the solenoid-operated valve and which inhibits, when a pressure difference obtained by subtracting, from a pressure of the hydraulic liquid in a first portion of the first liquid passage that is located between the relief value and the hydraulic suspension device, a pressure of the hydraulic liquid in a second portion of the first liquid passage that is located between the relief valve and the first accumulator does not exceed a pre-set pressure, the hydraulic liquid from flowing between the hydraulic suspension device and the first accumulator and, when the pressure difference exceeds the pre-set pressure, allows the hydraulic liquid to flow from the hydraulic suspension device to the first accumulator and inhibits the hydraulic liquid from flowing from the first accumulator
  • the solenoid-operated valve may be adapted such that when a great inertia force is applied to the vehicle, e.g., when a transverse-direction (i.e., lateral) acceleration or a longitudinal-direction acceleration of the vehicle is higher than a threshold value, the valve is switched from its open state to its closed state.
  • each of the first and second accumulators includes a housing; and a partition member which separates an inner space of the housing into two chambers one of which is located on a side of a corresponding one of the first and second liquid passages and provides a hydraulic chamber filled with the hydraulic liquid and an other of which is located opposite to the hydraulic chamber and provides a spring chamber elastically pressing, via the partition member, the hydraulic liquid filling the hydraulic chamber.
  • each of the first and second accumulators functions as a pressure-change absorbing device.
  • a suspension apparatus for use in a vehicle including a body, a body-side member, a wheel, and a wheel-side member, the apparatus comprising a hydraulic suspension device which is adapted to be provided between the body-side member and the wheel-side member; a first accumulator and a second accumulator which are connected, in parallel, to the hydraulic suspension device via a first liquid passage and a second liquid passage, respectively; and a liquid-flow control device which is provided in the first liquid passage and which controls a flow of a hydraulic liquid between the hydraulic suspension device and at least the first accumulator, wherein the first accumulator accommodates a first elastic body whose elastic deformation allows the hydraulic liquid to flow thereinto, the second accumulator accommodates a second elastic body whose elastic deformation allows the hydraulic liquid to flow thereinto, and the second elastic body has a spring constant higher than a spring constant of the first elastic body, and wherein the liquid-flow control device is selectively operable in (a) a low spring constant mode thereof in which the liquid-flow control
  • the present suspension apparatus may employ any of the technical features in accordance with the modes (1) through (7).
  • the invention also provides a vehicle comprising the suspension apparatus of any preceding mode.
  • suspension apparatus as an embodiment of the present invention by reference to the drawings.
  • four suspension apparatuses each according to the invention are provided for four wheels (i.e., left and right front wheels and left and right rear wheels) of a vehicle, respectively, one of the four suspension apparatuses that is provided for, e.g., the left front wheel will be described as a representative of the four apparatuses, and description of the other, three apparatuses is omitted.
  • reference numeral 10 designates a shock absorber as a hydraulic suspension device (so-called “hydraulic suspension cylinder”) that is provided, for a left front wheel 12 of an automotive vehicle, between a wheel-side member 14 and a body-side member 16.
  • the wheel-side member 14 is provided on the side of the left front wheel 12, and the body-side member 16 is provided on the side of a body of the vehicle.
  • the shock absorber 10 includes a cylindrical housing 20, a piston 22 that is slideably received in the housing 20, and a piston rod 24 that is connected, at one of opposite ends thereof, to the piston 24.
  • the housing 20 is connected to the wheel-side member 14 such that the housing 20 is not movable relative to the same 14 in an upward or a downward direction; and the piston rod 24 is connected, at the other end thereof, to the body-side member 16 such that the piston rod 24 is not movable relative to the same 16 in the upward or downward direction.
  • an inner space of the housing 20 is separated by the piston 22 into two hydraulic chambers 30, 32, and the piston 22 has a communication passage 34 as a restrictor passage that includes a restrictive portion and connects between the two hydraulic chambers 30, 32.
  • a corresponding one of the housing 20 and the piston 22 is moved relative to the other in the same direction.
  • the shock absorber 10 exhibits a damping effect corresponding to a speed of movement of the piston 22 relative to the housing 20.
  • a damping-characteristic control actuator not shown, changes a cross-section area of the communication passage 34, and thereby controls a damping characteristic of the shock absorber 10.
  • One 32 of the two hydraulic chambers 30, 32 of the shock absorber 10 is connected, in parallel, to a first and a second accumulator 42, 44 via a flow passage 40.
  • each of the first and second accumulators 42, 44 includes a housing 48, and a flexible partition member 50 that separates an inner space of the housing 48 into two chambers, i.e., a hydraulic chamber 52 located on the side of the flow passage 40, and a gas chamber 54 located opposite to the hydraulic chamber 52.
  • the hydraulic chamber 52 is filled with a hydraulic liquid
  • the gas chamber 54 accommodates a pressurized gas (e.g., a high-pressure air) functioning as an elastic body
  • a pressure of the liquid in the hydraulic chamber 52 and a pressure of the gas in the gas chamber 54 are kept equal to each other.
  • Fig. 2 shows a state in which the hydraulic chamber 52 is filled with a certain amount of the hydraulic liquid.
  • the respective gas chambers 54 of the first and second accumulators 42, 44 are constructed such that when respective pressures of the respective pressurized gases filling the two gas chambers 54 are equal to each other, a volume of the gas filling the gas chamber 54 of the second accumulator 44, i.e., a volume of the gas chamber 54 of the second accumulator 44 is smaller than that of the gas chamber 54 of the first accumulator 42. Therefore, the second accumulator 44 has a higher spring constant than that of the first accumulator 42.
  • the flow passage 40 includes a common passage 60, and a first and a second individual passage 62, 64 that are connected to the first and second accumulators 42, 44, respectively.
  • the shock absorber 10 and the first accumulator 42 are connected to each other by the common passage 60 and the first individual passage 62; and the shock absorber 10 and the second accumulator 44 are connected to each other by the common passage 60 and the second individual passage 64.
  • the common passage 60 and the first individual passage 62 cooperate with each other to provide a first liquid passage
  • the second individual passage 64 provides a second liquid passage.
  • the second individual passage 64 is connected to a connection point or portion 66 of the first liquid passage 60, 62.
  • a liquid-flow control device 70 is provided in the first individual passage 62.
  • the liquid flow control device 70 includes a solenoid-operated open/close valve 72 and a relief valve 74 which are connected, in parallel, to the first individual passage 62.
  • the solenoid-operated open/close valve 72 includes a solenoid, and is a normally open valve that is normally in an open state thereof and is switchable between the open state and a closed state thereof by controlling an electric current supplied to the solenoid.
  • the relief valve 74 is switched from a closed state thereof to an open state thereof when a pressure difference obtained by subtracting, from the pressure of the hydraulic liquid in a first portion of the first individual passage 62 that is located on the side of the shock absorber 10, the pressure of the hydraulic liquid in a second portion of the first individual passage 62 that is located on the side of the first accumulator 42, exceeds a pre-set liquid pressure (hereinafter, referred to as the "relief pressure").
  • a flow passage in a connection portion (hereinafter, referred to as the "first connection portion") 68 of the first accumulator 42 that is connected to the first individual passage 62 has a transverse cross-section area S J1 (hereinafter, referred to as the "first flow area S J1 "), and a flow passage in a connection portion (hereinafter, referred to as the "second connection portion") 67 of the second accumulator 44 that is connected to the second individual passage 64 has a transverse cross-section area S J2 (hereinafter, referred to as the "second flow area S J2 ") that is smaller than the first flow area S J1 ⁇
  • the first individual passage 62 has a transverse cross-section area, i.e., a third flow area S P1
  • the second individual passage 64 has a transverse cross-section area, i.e., a fourth flow area S P2 that is equal to the third flow area S P1 and is larger than the first and second flow areas S J1 ,
  • the present suspension apparatus additionally employs a suspension ECU (electronic control unit) 80 that is essentially constituted by a computer and includes an implementing portion 84, a memory portion 84, and an input/output (I/O) portion 86.
  • a suspension ECU electronic control unit
  • I/O input/output
  • the memory portion 84 stores a valve control program represented by a flow chart shown in Fig. 3.
  • the valve control program shown in Fig. 3 is periodically implemented at a pre-set interval of time.
  • Step S1 the suspension ECU 80 obtains the lateral acceleration of the vehicle, detected by the lateral-acceleration sensor 88.
  • Step S2 the ECU 80 judges whether the obtained lateral acceleration is higher than a threshold value. If a negative judgment is made at Step S2, the control of the ECU 80 goes to Step S3 to switch the solenoid-operated open/close valve 72 to the open state thereof, and, if a positive judgment is made at Step S2, the control of the ECU 80 goes to Step S4 to switch the open/close valve 72 to the closed state thereof.
  • the shock absorber 10 When the solenoid-operated open/close valve 72 is in its open state, the shock absorber 10 is in communication with both the first and second accumulators 42, 44, as shown in Fig. 4A.
  • the change of pressure of the first accumulator 42 e.g., the change of pressure of the gas in the gas chamber 54 thereof and the change of pressure of the second accumulator 44 are equal to each other.
  • the piston 22 of the shock absorber 10 is moved in the upward or downward direction, and accordingly the shock absorber 10 communicates respective amounts of the hydraulic liquid with the first and second accumulators 42, 44.
  • the first and second accumulators 42, 44 as a whole exhibit a low spring constant, as indicated at broken line in Fig. 5.
  • the present suspension apparatus can improve the riding comfort of a driver of the vehicle.
  • the shock absorber 10 cannot communicate with the first accumulator 42, and is in communication with the second accumulator 44 only, as shown in Fig. 4B.
  • the shock absorber 10 communicates some amount of the hydraulic liquid with the second accumulator 44 only.
  • the second accumulator 44 exhibits the higher spring constant than that of the two accumulators 42, 44 as a whole, as indicated at solid line in Fig. 5.
  • the spring constant of the second accumulator 44 per se is higher than that of the first accumulator 42 per se.
  • Fig. 5 shows a timewise change of the gas pressure in the respective gas chambers 54 of the first and second accumulators 42, 44 (corresponding to Fig. 4A), and a timewise change of the gas pressure in the gas chamber 54 of the second accumulator 44 (corresponding to Fig. 4B), under the condition that a system pressure (i.e., the pressure of the hydraulic liquid in the flow passage 40) does not exceed the above-described relief pressure.
  • a system pressure i.e., the pressure of the hydraulic liquid in the flow passage 40
  • the spring constant of the first and second accumulators 42, 44 as a whole is decreased, and accordingly a slope of increase of the pressure in the second accumulator 44 is decreased, as compared with the state, indicated at broken line, in which the relief valve 74 is in its closed state.
  • the system pressure can be effectively prevented from being excessively increased, which leads to increasing the life expectancy of a piping system defining the flow passage 40 and the life expectancy of the present suspension apparatus as a whole.
  • the hydraulic liquid can more easily flow into the first accumulator 42 than into the second accumulator 44. Therefore, as shown in Figs. 6B and 6C, when a certain amount of the hydraulic liquid flows out of the shock absorber 10, the more amount of the liquid flows into the first accumulator 42 than into the second accumulator 44 and accordingly the slope of change, or the amount of increase, of the liquid pressure in the second accumulator 44 is smaller than that of the liquid pressure in the first accumulator 42. Therefore, as indicated at one-dot chain line and two-dot chain line in Fig. 6A, the system pressure can be effectively prevented from being excessively increased, by making it easier for the hydraulic liquid to flow into the first accumulator 42.
  • the hydraulic liquid can more easily flow into the first accumulator 42 than into the second accumulator 44.
  • this effect can be obtained by making the first individual passage 62 shorter than the second individual passage 64.
  • the solenoid-operated open/close valve 72 is opened and closed based on the lateral acceleration of the vehicle.
  • the solenoid-operated open/close valve 72 may be adapted to be opened and closed based on an acceleration of the vehicle in a forward or a backward direction. If the stroke of the shock absorber 10 is restrained when the forward/backward acceleration of the vehicle is high, the pitching of the body of the vehicle can be reduced.
  • the liquid-flow control device 70 may be modified in various manners.
  • the solenoid-operated open/close valve 72 may be replaced with a solenoid-operated direction control valve.
  • the solenoid-operated open/close valve 72 and the relief valve 74 may be integrated with each other.
  • Each of the first and second accumulators 42, 44 is not limited to the above-described bladder type.
  • each accumulator 42, 44 may be of a bellows type, a diaphragm type, or a piston type.
  • the two accumulators 42, 44 may be of different types.
  • the shock absorber 10 is employed as the hydraulic suspension device.
  • an elastic-force producing device that produces an elastic force corresponding to an amount of displacement of one of the wheel-side member 14 and the body-side member 16 relative to the other in the upward or downward direction may be employed as the hydraulic suspension device.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Vehicle Body Suspensions (AREA)
EP05255290A 2004-09-21 2005-08-26 Aufhängungseinrichtung Expired - Fee Related EP1637368B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2004273398A JP2006088754A (ja) 2004-09-21 2004-09-21 サスペンション装置

Publications (3)

Publication Number Publication Date
EP1637368A2 true EP1637368A2 (de) 2006-03-22
EP1637368A3 EP1637368A3 (de) 2006-05-17
EP1637368B1 EP1637368B1 (de) 2012-06-13

Family

ID=35462641

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05255290A Expired - Fee Related EP1637368B1 (de) 2004-09-21 2005-08-26 Aufhängungseinrichtung

Country Status (4)

Country Link
US (1) US7546911B2 (de)
EP (1) EP1637368B1 (de)
JP (1) JP2006088754A (de)
CN (1) CN100465004C (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2258961A3 (de) * 2009-06-05 2017-10-11 Fox Factory, Inc. Vorrichtung und Verfahren für einen Fahrzeugstoßdämpfer

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003066859A2 (en) * 2002-02-07 2003-08-14 Yissum Research Development Company Of The Hebrew University Of Jerusalem Amino acid sequences capable of facilitating penetration across a biological barrier
SE532590C2 (sv) 2007-11-09 2010-03-02 Bae Systems Haegglunds Ab Fjädringsanordning samt förfarande vid fjädring och/eller dämpning för fordon
US8636120B1 (en) * 2010-08-20 2014-01-28 Sturman Industries, Inc. Active and semi-active ride control with energy recovery
US9371879B2 (en) * 2013-10-31 2016-06-21 Itt Manufacturing Enterprises Llc Pseudo-linear hydro-pneumatic spring
US9670979B1 (en) * 2016-05-13 2017-06-06 Liquidspring Technologies, Inc. Resilient expandable pressure vessel
JP6328694B2 (ja) * 2016-05-31 2018-05-23 アイシン精機株式会社 エアサスペンション装置
CN108425980A (zh) * 2017-02-14 2018-08-21 贺德克国际有限公司 液压气动式活塞缸装置
DE102018118911A1 (de) * 2018-08-03 2020-02-06 Thyssenkrupp Ag Schwingungsdämpfer, Fahrzeug, Verwendung eines Absperrventils und Verfahren zum Befüllen
CN217598270U (zh) * 2021-12-30 2022-10-18 比亚迪股份有限公司 液压式主动悬架及具有其的车辆

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6349512A (ja) 1986-08-19 1988-03-02 Tokico Ltd 油圧サスペンシヨン装置
JPS6378806A (ja) 1986-09-19 1988-04-08 Tokico Ltd サスペンシヨン装置
JPS63130419A (ja) 1986-11-20 1988-06-02 Tokico Ltd 油圧サスペンシヨン装置

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2436030A1 (fr) * 1978-09-12 1980-04-11 Leduc & Fils Rene Perfectionnements aux dispositifs de suspension hydro-pneumatique pour vehicules
JPS59177842A (ja) 1983-03-29 1984-10-08 Matsushita Electric Ind Co Ltd 平板形陰極線管
JPS6121814A (ja) 1984-07-09 1986-01-30 Kayaba Ind Co Ltd ガスバネの圧力調整装置
US4693493A (en) * 1985-10-22 1987-09-15 Toyota Jidosha Kabushiki Kaisha System for vehicle body roll control utilizing steering angle detection
JPH082727B2 (ja) * 1988-01-26 1996-01-17 日産自動車株式会社 アクティブサスペンション用油圧回路
US4958850A (en) * 1988-03-03 1990-09-25 Toyota Jidosha Kabushiki Kaisha Hydraulic circuit system for a vehicle height control device
JP2541353B2 (ja) 1990-09-18 1996-10-09 三菱自動車工業株式会社 車両用アクティブサスペンション装置
US5188390A (en) * 1991-12-16 1993-02-23 Ford Motor Company Suspension system having active and passive modes
JP3336088B2 (ja) 1993-09-17 2002-10-21 株式会社ショーワ 車両のサスペンション装置
DE19748224B4 (de) * 1997-10-31 2005-07-14 Deere & Company, Moline Hydropneumatische Achsfederung für angetriebene Fahrzeugachsen
DE10112082B4 (de) * 2001-03-12 2009-05-07 Carl Freudenberg Kg Hydropneumatische niveaugeregelte Achsfederung an Fahrzeugen insbesondere für vollgefederte Fahrzeuge

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6349512A (ja) 1986-08-19 1988-03-02 Tokico Ltd 油圧サスペンシヨン装置
JPS6378806A (ja) 1986-09-19 1988-04-08 Tokico Ltd サスペンシヨン装置
JPS63130419A (ja) 1986-11-20 1988-06-02 Tokico Ltd 油圧サスペンシヨン装置

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2258961A3 (de) * 2009-06-05 2017-10-11 Fox Factory, Inc. Vorrichtung und Verfahren für einen Fahrzeugstoßdämpfer
US10240655B2 (en) 2009-06-05 2019-03-26 Fox Factory, Inc. Apparatus and methods for a vehicle shock absorber
US10704640B2 (en) 2009-06-05 2020-07-07 Fox Factory, Inc. Apparatus and methods for a vehicle shock absorber

Also Published As

Publication number Publication date
EP1637368A3 (de) 2006-05-17
US20060060438A1 (en) 2006-03-23
CN1751905A (zh) 2006-03-29
CN100465004C (zh) 2009-03-04
EP1637368B1 (de) 2012-06-13
US7546911B2 (en) 2009-06-16
JP2006088754A (ja) 2006-04-06

Similar Documents

Publication Publication Date Title
EP1637368B1 (de) Aufhängungseinrichtung
US20020121416A1 (en) Hydraulic cylinder apparatus
US5013061A (en) Hydraulic circuit for actively controlled automotive suspension system with fail-safe system
EP1707407A1 (de) Luftfederung und elektronisch gesteuertes Aufhängungssystem
EP1659007B1 (de) Luftfederung und elektronisch gesteuertes Aufhängungssystem
US10682893B2 (en) Spring- and damping arrangement for a motorcycle
JPH0662052B2 (ja) 車輪懸架装置のためのばね機構
CN109476200B (zh) 改进的悬架
US7273209B2 (en) Suspension apparatus
JPH01122717A (ja) 能動型サスペンション装置
CN101349316A (zh) 感载变阻尼或可控感载变阻尼减震系统
US10343480B2 (en) Suspension system
US7210688B2 (en) Suspension system for motor vehicle
EP1628039B1 (de) Hydraulischer Stossdämpfer
JP6361414B2 (ja) 車両のサスペンション装置
JP4442556B2 (ja) 車高調整装置および液圧源制御装置
JP4631528B2 (ja) サスペンション装置
JP4517897B2 (ja) 車高調整装置
JPS6045416A (ja) 自動車のサスペンション
JPH10203128A (ja) 車高調整装置
WO2004111488A1 (ja) 車両用油圧式緩衝装置
CN115450968A (zh) 一种主动式液压升降控制系统
JP2534609Y2 (ja) サスペンション装置
JPH07228118A (ja) 流体圧式アクティブサスペンション
JP4449887B2 (ja) サスペンション装置

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20050909

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK YU

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK YU

AKX Designation fees paid

Designated state(s): DE FR GB

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

RIN1 Information on inventor provided before grant (corrected)

Inventor name: HONMA, MOTOHIKOC/O TOYOTA JIDOSHA K.K.

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602005034644

Country of ref document: DE

Effective date: 20120809

RAP2 Party data changed (patent owner data changed or rights of a patent transferred)

Owner name: TOYOTA JIDOSHA KABUSHIKI KAISHA

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20130314

REG Reference to a national code

Ref country code: GB

Ref legal event code: 746

Effective date: 20130520

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602005034644

Country of ref document: DE

Effective date: 20130314

REG Reference to a national code

Ref country code: DE

Ref legal event code: R084

Ref document number: 602005034644

Country of ref document: DE

Effective date: 20130522

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 12

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 13

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20170714

Year of fee payment: 13

Ref country code: GB

Payment date: 20170823

Year of fee payment: 13

Ref country code: DE

Payment date: 20170822

Year of fee payment: 13

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 602005034644

Country of ref document: DE

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20180826

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190301

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180831

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180826